CN1493800A - Long outage intermittent motion linkage basic structure and its designing method - Google Patents
Long outage intermittent motion linkage basic structure and its designing method Download PDFInfo
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- CN1493800A CN1493800A CNA031506739A CN03150673A CN1493800A CN 1493800 A CN1493800 A CN 1493800A CN A031506739 A CNA031506739 A CN A031506739A CN 03150673 A CN03150673 A CN 03150673A CN 1493800 A CN1493800 A CN 1493800A
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Abstract
A basic structure and design method for an intermittently moving connecting rod mechanism with long stop time feature that on the basis of the 4-rod mechanism pivoted in a plane, the different-type advanced reciprocating swinging mechanism is serially connected. The reciprocating swinging output member is fixed to the moving member ED of said 4-rod mechanism to make the moving member ED do reciprocating swinging in an angle range.
Description
Technical field
The invention belongs to the mechanical mechanism technical field, be specifically related to a kind of length and rest the basic structure and the design method thereof of linkage mechanism.
Background technique
Intermittent motion mechanism's kind commonly used has ratchet, sheave, intermittent gearing mechanism, cam mechanism etc.They are simple in structure, manufacturing technology is ripe, have been widely used in occasions such as various mechanical automation manufacturing mechanisms and production line.But generally there are noise in ratchet, sheave, intermittent gearing mechanism and impact shortcomings such as bigger, the occasion that the speed that is unsuitable for is higher; Cam mechanism can be realized intermittent movement requirement arbitrarily in theory, and design freedom is higher, but its higher pair contact power transmission, easy to wear, and its design and the general support that be unable to do without modern CAD/CAM technology of manufacturing.
Linkage mechanism has low auxiliary driving, wear-resistant, easy to manufacture, characteristics such as cost is low, can obtain approximate dwell linkage mechanism by the Mechanism Optimization design, and many application are also arranged in some manufacturing machines.But its synthesis of mechanism is general harder to tackle and can only realize that mostly the approximate of short period rest.Therefore, seek simple in structure, design is more convenient, have longer down-time period and higher novel intermittent movable connecting rod mechanism of resting precision, has important practical usage.
Invention description
The object of the invention be to propose a kind of simple in structure, have longer down-time period and higher intermittent motion mechanism's connecting rod basic structure and a design method thereof of resting precision.
The dwell linkage mechanism basic structure that the present invention proposes is made of a planar pivot four-bar mechanism preposition reciprocally swinging mechanism of series connection.As shown in Figure 1, among the planar pivot four-bar mechanism DEFG, note a=DE is input bar, b=EF, c=FG is take-off lever, and d=DG is frame, and D, E, F, G are hinge point, bar covers with foot and states condition: a=d, b=c, c ≠ d, d＜c, 0.2%≤(c-d)/d≤10%; The reciprocally swinging output link of above-mentioned preposition reciprocally swinging mechanism connects firmly mutually with the motion bar ED of planar pivot four-bar mechanism DEFG.Mechanism's pattern of this preposition reciprocally swinging mechanism can be any mechanism of output reciprocally swinging, comprises the arbitrary plane mechanism or the spatial mechanism that export reciprocally swinging, also can be driving mechanisms such as electromagnet or motor.
The composite mechanism that above-mentioned preposition reciprocally swinging mechanism and above-mentioned planar pivot four-bar mechanism are composed in series, can make the take-off lever FG output of fourbar linkage that the intermittent reciprocating swing of the long section of resting is arranged, and it rest precision and depend primarily on the long x=(c-d) of difference of relative bar/d of fourbar linkage.X is more little, and then the fluctuation of the pivot angle β of output link FG is more little in the section of resting, and the precision of promptly resting is high more.Shown in embodiment 1,2.
Particularly, the composite mechanism that adopts preposition reciprocally swinging spatial mechanism and aforementioned planar pivot four-bar mechanism to be in series, easily the position, implementation space intersect or alternating axis between length rest transmission.
Principle of the present invention is as follows: as shown in Figure 1, the angle of note input bar ED and frame DG is that input angle is φ, the angle of note take-off lever FG and frame DG is that input angle is β, and then under the bar elongate member of above-mentioned planar pivot four-bar mechanism, the form of β-φ angular displacement curve as shown in Figure 2.As seen, the long down-time period that exists the β angle to change with the φ angle hardly on the curve is as the HJ section among Fig. 2 or H ' J ' section.Therefore, as long as according to designing requirement, preposition reciprocal swing-bar mechanism makes rotation-the rest section I-H-J section (or rest-rotational segment J '-H '-I ' section) of movable part ED along β shown in Figure 1-φ curve, promptly at φ
I≤ φ≤φ
J(or φ
J '≤ φ≤φ
I ') (φ
I, φ
J, φ
J ', φ
I '≠ 2 π k, k=0,1,2 ...) the angle of oscillation scope in make reciprocally swinging, can obtain required dwell linkage mechanism.
It is as follows that above-mentioned novel length is rested the design procedure of linkage mechanism:
(1) selects suitable preposition reciprocally swinging mechanism by actual conditions (as angle of oscillation scope, mechanism's pattern restrictive condition etc.);
(2) by mechanism's output movement rest the precision and the requirement such as segment limit that rests, adjust each structural parameter, and carry out kinematic analysis of mechanisms, finally determine suitable (c-d)/d value and other mechanism structure parameter; Kinematic analysis of mechanisms in the above-mentioned steps can be realized on computers by special written program.This analysis can be a kind of visual motion analysis.
Because the precision of resting of above-mentioned composite mechanism depends primarily on long poor (the c-d)/d of relative bar of above-mentioned planar pivot four-bar mechanism, so easily by resting definite (the c-d)/d value of required precision.Design process does not need loaded down with trivial details Mechanism Optimization design method, is suitable for engineering design application.
Description of drawings
Fig. 1 is a planar pivot four-bar mechanism basic block diagram of the present invention.
Fig. 2 is Kinematic Analysis figure among Fig. 1.
Fig. 3 is the dwell linkage mechanism structural drawing that preposition mechanism adopts crankrocker mechanism.
Fig. 4 is Kinematic Analysis figure among Fig. 3.
Fig. 5 is the dwell linkage mechanism structural drawing that preposition mechanism adopts oscillating guidebar mechanism.
Fig. 6 is Kinematic Analysis figure among Fig. 5.
Embodiment
Embodiment 1
Crankrocker mechanism is got by preposition mechanism, as shown in Figure 3.Table 1 is depicted as long poor (the c-d)/d of different bars to resting the impact analysis of precision.
Rest precision analysis during the preposition crankrocker mechanism of table 1
| x＝(c-d)/d(％) | The section of resting, θ | Δθ | ?β max | ??β min | Δβ＝β max-β min | Rest error delta β/Δ θ (%) |
| ????3％ | 153°～323° | 170° | ?176.93° | ?174.74° | ????2.19° | ????1.3％ |
| ????1％ | 153°～323° | 170° | ?178.92° | ?178.04° | ????0.88° | ????0.517％ |
| ????0.5％ | 153°～323° | 170° | ?179.45° | ?178.99° | ????0.46° | ????0.271％ |
| ????0.2％ | 153°～323° | 170° | ?179.78° | ?179.58° | ????0.20° | ????0.118％ |
Wherein the mechanism structure parameter is for example down:
a
1＝100，b
1＝140，c
1＝120，d
1＝140，a＝d＝100，b＝c＝100.2～103mm，α
0＝20°，α
1＝90°。
a
1=AB is a crank, b
1=BC is a connecting rod, c
1=CD is a rocking bar, d
1=AD is a frame, α
0Be the angle of the frame DG of the frame AD of preposition mechanism and rearmounted mechanism, α
1Angle for the input bar ED of the rocking bar CD of preposition mechanism and rearmounted mechanism.
Embodiment 2
Oscillating guidebar mechanism is got by preposition mechanism, as shown in Figure 5.Table 2 is depicted as long poor (the c-d)/d of different bars relatively to resting the impact analysis of precision.
When adopting preposition oscillating guidebar mechanism, table 2 rests precision analysis
| x＝(c-d)/d(％) | The section of resting, θ | Δθ | ??β max | ??β min | Δβ＝β max-β min | Rest error delta β/Δ θ (%) |
| ????3％ | 211°～357° | 146° | ??178.91° | ?175.04° | ????3.87° | ????2.65％ |
| ????1％ | 211°～357° | 146° | ??179.63° | ?178.01° | ????1.62° | ????1.11％ |
| ??0.5％ | 211°～357° | 146° | ??179.81° | ?178.94° | ????0.87° | ????0.6％ |
| ??0.2％ | 211°～357° | 146° | ??179.92° | ?179.55° | ????0.37° | ????0.25％ |
Wherein, the mechanism structure parameter is as follows: a
2=100, d
2=120, a=d=100, b=c=100.2～103mm, α
0=60 °, α
1=60 °.D
2=AD is a preposition mechanism frame, a
2=AB is a crank, α
0Be the angle of the frame DG of the frame AD of preposition mechanism and rearmounted mechanism, α
1Angle for the input bar ED of the take-off lever BD of preposition mechanism and rearmounted mechanism.
By table 1, table 2 as seen, resting precision depends primarily on the value of the long difference of relative bar x=(c-d)/d of fourbar linkage among Fig. 1.(c-d)/and d is more little, and the precision of then resting is high more.But as previously mentioned, mechanism should satisfy a=d, b=c, c ≠ d, the condition of d＜c.Consider the restriction of general revolute pair machining accuracy and matching gap, can be in the scope of 0.2%≤(c-d)/d≤10% choose suitable (c-d)/d value by resting the precision and the segment limit requirement that rests.
Claims (4)
1, a kind of dwell linkage mechanism basic structure is characterized in that being made of a planar pivot four-bar mechanism preposition reciprocally swinging mechanism of series connection; Fourbar linkage DEFG each bar a, b, c, d satisfy following relation: a=d, b=c, and c ≠ d, d＜c, 0.2%≤(c-d)/d≤10%, a=DE is the input bar here; B=EF is connecting rod; C=FG is take-off lever; D=DG is by frame (fixing rod); D, E, F, G are hinge point; The output link of preposition reciprocal swing-bar mechanism connects firmly mutually with the input bar DE of fourbar linkage.
2, according to the basic structure of the described dwell linkage mechanism of claim 1, it is characterized in that planar mechanism or the spatial mechanism of described preposition reciprocally swinging mechanism for the output reciprocally swinging, or driving mechanisms such as electromagnet or motor.
3, dwell linkage mechanism basic structure according to claim 2 is characterized in that described preposition reciprocal swinging mechanism is crankrocker mechanism or oscillating guidebar mechanism.
4, a kind of design method of dwell linkage mechanism is characterized in that concrete steps are as follows:
(1) selects suitable preposition reciprocally swinging mechanism by actual conditions;
(2) by mechanism's output movement rest the precision and the requirement such as segment limit that rests, adjust each structural parameter, and carry out kinematic analysis of mechanisms, finally determine suitable (c-d)/d value and other mechanism structure parameter; Kinematic analysis of mechanisms in the above-mentioned steps can be realized on computers by special written program.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA031506739A CN1493800A (en) | 2003-08-29 | 2003-08-29 | Long outage intermittent motion linkage basic structure and its designing method |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA031506739A CN1493800A (en) | 2003-08-29 | 2003-08-29 | Long outage intermittent motion linkage basic structure and its designing method |
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|---|---|
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ID=34240593
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|---|---|---|---|
| CNA031506739A Pending CN1493800A (en) | 2003-08-29 | 2003-08-29 | Long outage intermittent motion linkage basic structure and its designing method |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103133623A (en) * | 2013-01-29 | 2013-06-05 | 中国矿业大学 | Magnetorheological fluid rotation pair and connecting rod mechanism thereof |
| CN103398150A (en) * | 2013-06-24 | 2013-11-20 | 南京航空航天大学 | Space crank-rocker mechanism capable of moving intermittently |
| CN106391227A (en) * | 2016-11-16 | 2017-02-15 | 许国梁 | Efficient plastic garbage cutting-up equipment for battery production |
| CN108789957A (en) * | 2018-07-04 | 2018-11-13 | 胡兴旺 | A kind of plastic products reclaimer |
| CN112610672A (en) * | 2020-12-08 | 2021-04-06 | 安徽工程大学 | Design method of crank and rocker mechanism of rotation and reciprocating swing conversion device |
-
2003
- 2003-08-29 CN CNA031506739A patent/CN1493800A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103133623A (en) * | 2013-01-29 | 2013-06-05 | 中国矿业大学 | Magnetorheological fluid rotation pair and connecting rod mechanism thereof |
| CN103398150A (en) * | 2013-06-24 | 2013-11-20 | 南京航空航天大学 | Space crank-rocker mechanism capable of moving intermittently |
| CN103398150B (en) * | 2013-06-24 | 2016-08-10 | 南京航空航天大学 | One can space crank-rocker mechanism capable of moving intermittently |
| CN106391227A (en) * | 2016-11-16 | 2017-02-15 | 许国梁 | Efficient plastic garbage cutting-up equipment for battery production |
| CN108789957A (en) * | 2018-07-04 | 2018-11-13 | 胡兴旺 | A kind of plastic products reclaimer |
| CN112610672A (en) * | 2020-12-08 | 2021-04-06 | 安徽工程大学 | Design method of crank and rocker mechanism of rotation and reciprocating swing conversion device |
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